US20130213033A1 - Master cylinder for a regulated braking system - Google Patents
Master cylinder for a regulated braking system Download PDFInfo
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- US20130213033A1 US20130213033A1 US13/515,898 US201013515898A US2013213033A1 US 20130213033 A1 US20130213033 A1 US 20130213033A1 US 201013515898 A US201013515898 A US 201013515898A US 2013213033 A1 US2013213033 A1 US 2013213033A1
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- piston
- master cylinder
- control passages
- control
- passages
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- 230000001105 regulatory effect Effects 0.000 title claims abstract description 7
- 238000007789 sealing Methods 0.000 claims abstract description 30
- 238000000034 method Methods 0.000 claims description 5
- 238000001125 extrusion Methods 0.000 claims description 4
- 239000000463 material Substances 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000005355 Hall effect Effects 0.000 description 1
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/101—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic equalising arrangements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/232—Recuperation valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/236—Piston sealing arrangements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/38—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including valve means of the relay or driver controlled type
Definitions
- the invention relates to a master cylinder for a regulated braking system having at least one piston, which is movable in a housing and which is sealed off by means of a sealing element arranged in an annular groove of the housing from a pressure chamber, which can be connected to an unpressurized replenishment chamber by means of control passages formed in the piston.
- a master cylinder of this kind is known from DE 10 2004 057 137 A1, for example, wherein the control passages are provided as radial transverse holes of small cross section and an encircling inner groove is formed on an inner side in the region of the transverse holes in order to minimize the idle travel of the master cylinder and, at the same time, to reduce the throttling resistance by reducing the length of the transverse holes.
- a regulated braking system such as a braking system with anti-slip regulation (ASR) or an electronic stability program (ESP)
- ASR anti-slip regulation
- ESP electronic stability program
- a disadvantage of the first-mentioned solution is found to be the fact that the flow resistance is reduced in favor of the stability of the piston and, furthermore, that the provision of a large number of small transverse holes is economically disadvantageous.
- the second solution has the disadvantage that the idle travel (closing travel) of the master cylinder is increased by displacing the controlling lateral edge of the holes.
- the object is achieved by virtue of the fact that the control passages of at least one of the pistons have a control edge formed parallel to a piston end face. This makes it possible to increase the flow cross section of the control passages while keeping the closing travel the same, thereby making it possible to improve dynamic behavior during control interventions.
- the control passages are preferably provided as axial grooves on an outer side of the piston.
- the axial grooves offer the advantage that defined guidance of the sealing element on the outer side of the piston is ensured.
- a large contact area of the piston with the sealing element or the inner sealing lip thereof and, at the same time, a large groove cross section can be achieved if the axial grooves are provided in a dovetail shape.
- control passages are provided as radial apertures in the piston.
- guidance for the sealing element on the piston is provided.
- Parallelism can be produced in a simple manner if the control passages are provided in the piston by stamping.
- the piston is made of plastic, making the piston simple and economical to produce.
- Another advantageous embodiment envisages that the piston is produced by means of an extrusion process.
- the piston is preferably of cup-shaped design with a bottom, and a first, centrally arranged fixing element for a return spring of the piston is provided on an inner side of the bottom.
- a second, centrally arranged fixing element for a magnetic guide element is provided on an outer side of the bottom.
- FIG. 1 shows a master cylinder according to the invention in a first illustrative embodiment, having a first and a second piston, in longitudinal section;
- FIG. 2 shows a partial view of the second piston in accordance with FIG. 1 in three-dimensional representation
- FIG. 3 shows another partial view of the second piston in accordance with FIG. 1 in three-dimensional representation and in partial section;
- FIG. 4 shows another partial view of the second piston in accordance with FIG. 1 in three-dimensional representation
- FIG. 5 shows a master cylinder according to the invention in a second illustrative embodiment, having a first and a second piston, in longitudinal section;
- FIG. 6 shows a piston in a third illustrative embodiment in three-dimensional representation
- FIG. 7 shows an enlarged detail of the piston shown in FIG. 6 .
- FIG. 1 shows a longitudinal section through a master cylinder 1 according to the invention in a first illustrative embodiment, which is used in a regulated braking system with anti-slip regulation (ASR) and/or an electronic stability program (ESP), for example, and is of plunger- and tandem-type design.
- ASR anti-slip regulation
- ESP electronic stability program
- the master cylinder 1 comprises a first and a second piston 3 , 4 , which is movable in a housing 2 , wherein a sealing element 7 , 8 in the form of a circular ring and having an inner sealing lip 9 , 10 subject to dynamic forces and an outer sealing lip 11 , 12 subject to static forces is provided in an annular groove 5 , 6 of the housing 2 .
- the inner sealing lip 9 , 10 subject to dynamic forces rests by means of a first sealing surface on the piston 3 , 4
- the outer sealing lip 11 , 12 subject to static forces rests by means of a second sealing surface on a bottom of the annular groove 5 , 6 .
- An outer side 13 , 14 of the pistons 3 , 4 serves as a guide surface.
- a first and a second pressure chamber 15 , 16 are connected to an unpressurized pressure medium reservoir (not shown) via a pressure medium channel (not shown) and a replenishment chamber 17 , 18 in the housing 2 and via control passages 19 , 20 in a cup-shaped wall 21 , 22 of the first and the second piston 3 , 4 .
- the pistons 3 , 4 are preloaded by means of return springs 23 , 24 .
- the return spring 23 , 24 is in each case arranged at least partially within the cup-shaped wall 21 , 22 .
- a centric peg 25 projects centrally within the wall 21 of the first piston 3 , said peg ending before it emerges axially from the wall 21 .
- This end 26 is provided with a stop 27 for a sleeve 28 , which interacts with a collar 29 in such a way that the sleeve 28 can be telescoped to a limited extent relative to the peg 25 .
- the sleeve 28 is urged into the interior of the piston by the return spring 23 upon actuation.
- the stop 27 is preferably an annular disk, which is riveted—in particular wobble-riveted—to the peg 25 .
- the other end of the sleeve 28 has the dish-type collar 29 for contact with the return spring 23 .
- said piston has a first fixing element 32 , which extends centrally within the wall 22 from an inner side of the bottom 31 in order to fix and position the return spring 24 .
- the first piston 3 is moved in actuating direction A. During this process, the movement of the first piston 3 is transmitted to the second piston 4 by the return spring 23 .
- the control edges 33 , 34 (described in greater detail below) of the control passages 19 , 20 are in the region of the sealing elements 7 , 8 , i.e. the control edges 33 , 34 have been crossed, the “idle travel” (closing travel) of the master cylinder 1 has been traversed since no more pressure medium can pass from the replenishment chambers 17 , 18 into the pressure chambers 15 , 16 via the control passages 19 , 20 .
- the connection between the pressure chambers 15 , 16 and the pressure medium reservoir is interrupted, and pressure is built up in the pressure chambers 15 , 16 .
- the additional pressure medium is drawn from the pressure medium reservoir via the pressure medium channels, the replenishment chambers 17 , 18 , the control passages 19 , 20 and the pressure chambers 15 , 16 in the case of an ASR or ESP intervention in the unactuated state of the master cylinder 1 .
- additional pressure medium is also drawn in by flow across the outer sealing lips 11 , 12 of the sealing elements 7 , 8 since they are folded over in the direction of the inner sealing lips 9 , 10 by the intake pressure and, as a result, the sealing surface of the outer sealing lip 11 , 12 no longer rests on the bottom of the annular groove 5 , 6 .
- a radial encircling inner groove 35 is provided on an inner side of the piston 3 in order to reduce the throttling resistance, said groove shortening the length of the control passages 19 , which are provided as radial transverse holes.
- FIGS. 2 to 4 show partial views of the second piston 4 in an enlarged, partially sectioned three-dimensional representation.
- control passages 20 In order to enlarge the area of flow of the control passages 20 of the second piston 4 , the control passages 20 have a control edge 34 which is formed parallel to a piston end face 36 .
- control passages 20 are designed as axial grooves on the outer side 14 of the piston 4 . These can be introduced into the piston 4 in a simple manner, e.g. by forming or stamping, if the piston 4 is made of plastic, making the piston 4 simple and economical to produce.
- the stability of the piston 4 is not affected by the axial grooves since the piston 4 can have a relatively thick wall 22 , without disadvantages in respect of weight and other necessary properties.
- piston 4 be produced by means of an extrusion process.
- Aluminum can be provided as a material in this case, for example.
- parallel control edges 34 and also the axial grooves can be provided in a simple manner.
- one groove end 54 of the axial grooves can be of tapered design, and an embodiment with a radius (convex or concave) is likewise conceivable within the scope of the invention.
- Different groove shapes are also possible. These can be introduced into the piston 4 in a substantially dovetail shape, for example, as shown.
- the dovetail groove shape has the advantage that the contact surface of the piston 4 with the sealing element 8 or the inner sealing lip 10 thereof is enlarged and, at the same time, a large flow cross section can be formed through an enlarged diameter of the groove at the groove base.
- control passages 20 described furthermore have the advantage that a collar heel 37 of the sealing element 8 is guided in a defined manner on the outer side 14 of the piston 14 and cannot enter the control passages 20 . Such a risk would exist in the case of an encircling groove, for example.
- the first fixing element 32 is provided in the form of three arms, wherein the individual arms 38 are of beveled design to simplify the installation and positioning of the return spring 24 .
- FIG. 4 shows an external view of the bottom 31 of the second piston 4 . It is apparent that a second, centrally arranged fixing element 39 in the form of a circular projection extends from an outer side of the bottom 31 . This performs its function when, in accordance with the second embodiment described below and shown in FIG. 5 , the master cylinder 1 has a sensor arrangement for monitoring the position and movement of the piston 3 , and a magnetic guide element 40 rests on the second piston 4 .
- the magnetic guide element 40 illustrated in FIG. 5 rests by means of a flange-shaped portion 41 on the bottom 31 of the second piston 4 .
- a recess 42 which corresponds to the second fixing element 39 and by means of which the magnetic guide element 40 is fixed and positioned on the second piston 4 .
- the magnetic guide element 40 additionally has a peg-shaped portion 43 which points in the opposite direction to the peg 25 of the first piston 3 and which serves as a means for guiding a permanent magnet 44 .
- the magnet 44 serves as a signal transmitter for a position transmitter and generates a magnetic field radially in the direction of a sensor element (not shown)—preferably in the form of a Hall-effect sensor, a magnetoresistive sensor or a reed contact—which is provided at a fixed location on the housing 2 and can be connected to an electronic control unit (not shown) in order to permit position detection.
- a sensor element preferably in the form of a Hall-effect sensor, a magnetoresistive sensor or a reed contact
- the magnet 44 is ring-shaped and, as is apparent, is arranged between disks 45 , 46 of magnetic material on a cylindrical support 47 made of nonmagnetic material, which has a collar 48 for axial support of the magnet 44 .
- the support 47 with the magnet 44 is acted upon, on the one hand, by the return spring 23 of the first piston 3 and, on the other hand, by another spring means 49 , which is supported on the second piston 4 , with the result that the magnet 44 is as it were clamped between the pistons 3 , 4 and movable relative to the latter.
- the spring force of the return spring 23 is greater than the spring force of the other spring means 49 . This allows an actuation-induced displacement of the magnet 44 , even if the second piston 4 is fixed immovably due to a regulating operation affecting the vehicle dynamics.
- the embodiment described of the second piston 4 in the two illustrative embodiments offers the additional advantages that, for example, the overall length of the master cylinder 1 can be shortened by means of a shorter return spring 24 , and the master cylinder 1 has fewer individual components overall. It is furthermore also possible, within the scope of the invention, to design the first piston 3 with the control passages 20 described in the form of axial grooves and with the first fixing element 32 .
- FIGS. 6 and 7 show a piston 50 of a third illustrative embodiment, which can be provided as a first and/or as a second piston of the master cylinder 1 .
- control passages 51 of the piston 50 have a control edge 52 formed parallel to a piston end face 53 .
- the control passages 51 are provided as radial apertures in the piston 50 , which can be produced from plastic or by means of an extrusion process, as described above.
- the parallel control edge 52 has the advantage that the flow cross section of the control passages 52 can be enlarged while keeping the closing travel the same, thus improving the dynamic behavior of the master cylinder 1 during control interventions.
- the remaining shape of the control passages 51 can be adapted to the corresponding characteristics of the piston.
- control passages begin radially and continue as a groove which extends axially under the sealing element.
Abstract
Description
- The invention relates to a master cylinder for a regulated braking system having at least one piston, which is movable in a housing and which is sealed off by means of a sealing element arranged in an annular groove of the housing from a pressure chamber, which can be connected to an unpressurized replenishment chamber by means of control passages formed in the piston.
- A master cylinder of this kind is known from
DE 10 2004 057 137 A1, for example, wherein the control passages are provided as radial transverse holes of small cross section and an encircling inner groove is formed on an inner side in the region of the transverse holes in order to minimize the idle travel of the master cylinder and, at the same time, to reduce the throttling resistance by reducing the length of the transverse holes. - In the case of use in a regulated braking system, such as a braking system with anti-slip regulation (ASR) or an electronic stability program (ESP), additional pressure medium is drawn in from a pressure medium reservoir via the master cylinder by a pump in the case of a control intervention. The disadvantage here is that the small cross section of the transverse holes produces an excessive flow resistance, and the pressure medium required cannot be made available quickly enough to the pump.
- In order to reduce the flow resistance, there is the possibility, in the case of the known master cylinders, of providing a larger number of transverse holes or of optimizing the transverse holes in respect of the diameter thereof. However, a disadvantage of the first-mentioned solution is found to be the fact that the flow resistance is reduced in favor of the stability of the piston and, furthermore, that the provision of a large number of small transverse holes is economically disadvantageous. The second solution has the disadvantage that the idle travel (closing travel) of the master cylinder is increased by displacing the controlling lateral edge of the holes.
- It is therefore the underlying object of the invention to provide a master cylinder which is improved in respect of the stated disadvantages of the known master cylinder.
- According to the invention, the object is achieved by virtue of the fact that the control passages of at least one of the pistons have a control edge formed parallel to a piston end face. This makes it possible to increase the flow cross section of the control passages while keeping the closing travel the same, thereby making it possible to improve dynamic behavior during control interventions.
- The control passages are preferably provided as axial grooves on an outer side of the piston. The axial grooves offer the advantage that defined guidance of the sealing element on the outer side of the piston is ensured.
- A large contact area of the piston with the sealing element or the inner sealing lip thereof and, at the same time, a large groove cross section can be achieved if the axial grooves are provided in a dovetail shape.
- In contrast, an alternative embodiment of the invention makes provision for the control passages to be provided as radial apertures in the piston. Here too, guidance for the sealing element on the piston is provided.
- Parallelism can be produced in a simple manner if the control passages are provided in the piston by stamping.
- According to an advantageous embodiment of the invention, the piston is made of plastic, making the piston simple and economical to produce.
- Another advantageous embodiment envisages that the piston is produced by means of an extrusion process.
- The piston is preferably of cup-shaped design with a bottom, and a first, centrally arranged fixing element for a return spring of the piston is provided on an inner side of the bottom.
- If the master cylinder has a sensor arrangement for monitoring the position and movement of a piston, then, according to an advantageous embodiment, a second, centrally arranged fixing element for a magnetic guide element is provided on an outer side of the bottom.
- Further features, advantages and possible applications of the invention will emerge from the dependent claims and the following description of illustrative embodiments and with reference to the drawing.
- In the drawing, in which each of the figures is highly schematized:
-
FIG. 1 shows a master cylinder according to the invention in a first illustrative embodiment, having a first and a second piston, in longitudinal section; -
FIG. 2 shows a partial view of the second piston in accordance withFIG. 1 in three-dimensional representation; -
FIG. 3 shows another partial view of the second piston in accordance withFIG. 1 in three-dimensional representation and in partial section; -
FIG. 4 shows another partial view of the second piston in accordance withFIG. 1 in three-dimensional representation; -
FIG. 5 shows a master cylinder according to the invention in a second illustrative embodiment, having a first and a second piston, in longitudinal section; -
FIG. 6 shows a piston in a third illustrative embodiment in three-dimensional representation, and -
FIG. 7 shows an enlarged detail of the piston shown inFIG. 6 . -
FIG. 1 shows a longitudinal section through amaster cylinder 1 according to the invention in a first illustrative embodiment, which is used in a regulated braking system with anti-slip regulation (ASR) and/or an electronic stability program (ESP), for example, and is of plunger- and tandem-type design. - The
master cylinder 1 comprises a first and asecond piston housing 2, wherein asealing element 7, 8 in the form of a circular ring and having aninner sealing lip outer sealing lip annular groove 5, 6 of thehousing 2. Theinner sealing lip piston outer sealing lip annular groove 5, 6. Anouter side pistons - In an unactuated state of the
master cylinder 1, which is illustrated inFIG. 1 , a first and asecond pressure chamber replenishment chamber housing 2 and viacontrol passages shaped wall second piston pistons return springs - The
return spring shaped wall FIG. 1 , acentric peg 25 projects centrally within thewall 21 of thefirst piston 3, said peg ending before it emerges axially from thewall 21. Thisend 26 is provided with astop 27 for asleeve 28, which interacts with acollar 29 in such a way that thesleeve 28 can be telescoped to a limited extent relative to thepeg 25. In other words, thesleeve 28 is urged into the interior of the piston by thereturn spring 23 upon actuation. As is apparent, thestop 27 is preferably an annular disk, which is riveted—in particular wobble-riveted—to thepeg 25. The other end of thesleeve 28 has the dish-type collar 29 for contact with thereturn spring 23. - At the
bottom 31 of thesecond piston 4, said piston has afirst fixing element 32, which extends centrally within thewall 22 from an inner side of thebottom 31 in order to fix and position thereturn spring 24. - To actuate the
master cylinder 1, thefirst piston 3 is moved in actuating direction A. During this process, the movement of thefirst piston 3 is transmitted to thesecond piston 4 by thereturn spring 23. As soon as thecontrol edges 33, 34 (described in greater detail below) of thecontrol passages sealing elements 7, 8, i.e. thecontrol edges master cylinder 1 has been traversed since no more pressure medium can pass from thereplenishment chambers pressure chambers control passages pressure chambers pressure chambers - In the case of an ASR or ESP intervention, it may be necessary to draw additional pressure medium in the direction of the wheel brakes from the pressure medium reservoir via the pressure chamber or
chambers pistons pressure chambers master cylinder 1 or to the wheel brakes in order to deliver in the direction of the wheel brakes or in the direction of the master cylinder 1 (recirculation principle). For this purpose, the additional pressure medium is drawn from the pressure medium reservoir via the pressure medium channels, thereplenishment chambers control passages pressure chambers master cylinder 1. In the case of an ESP intervention in the actuated state of themaster cylinder 1, additional pressure medium is also drawn in by flow across theouter sealing lips sealing elements 7, 8 since they are folded over in the direction of theinner sealing lips outer sealing lip annular groove 5, 6. In order to make available sufficient pressure medium quickly to the pump in the case of an ASR or ESP intervention, especially in the unactuated state of themaster cylinder 1, it is necessary to minimize the flow resistance of thecontrol passages master cylinder 1 should also be kept as small as possible. - In the region of the
control passages 19 of thefirst piston 3, a radial encirclinginner groove 35 is provided on an inner side of thepiston 3 in order to reduce the throttling resistance, said groove shortening the length of thecontrol passages 19, which are provided as radial transverse holes. -
FIGS. 2 to 4 show partial views of thesecond piston 4 in an enlarged, partially sectioned three-dimensional representation. - In order to enlarge the area of flow of the
control passages 20 of thesecond piston 4, thecontrol passages 20 have acontrol edge 34 which is formed parallel to apiston end face 36. - This makes it possible to enlarge the flow cross section of the
control passages 20 while keeping the closing travel the same, thus enabling the dynamic behavior of themaster cylinder 1 to be improved during control interventions. - As is apparent, the
control passages 20 according to the illustrative embodiment shown are designed as axial grooves on theouter side 14 of thepiston 4. These can be introduced into thepiston 4 in a simple manner, e.g. by forming or stamping, if thepiston 4 is made of plastic, making thepiston 4 simple and economical to produce. The stability of thepiston 4 is not affected by the axial grooves since thepiston 4 can have a relativelythick wall 22, without disadvantages in respect of weight and other necessary properties. - An alternative embodiment envisages that the
piston 4 be produced by means of an extrusion process. Aluminum can be provided as a material in this case, for example. Here too, theparallel control edges 34 and also the axial grooves can be provided in a simple manner. - As shown in
FIG. 3 , onegroove end 54 of the axial grooves can be of tapered design, and an embodiment with a radius (convex or concave) is likewise conceivable within the scope of the invention. Different groove shapes are also possible. These can be introduced into thepiston 4 in a substantially dovetail shape, for example, as shown. The dovetail groove shape has the advantage that the contact surface of thepiston 4 with thesealing element 8 or theinner sealing lip 10 thereof is enlarged and, at the same time, a large flow cross section can be formed through an enlarged diameter of the groove at the groove base. - However, rectangular, undulating, round or V-shaped grooves are also possible.
- The
control passages 20 described furthermore have the advantage that acollar heel 37 of thesealing element 8 is guided in a defined manner on theouter side 14 of thepiston 14 and cannot enter thecontrol passages 20. Such a risk would exist in the case of an encircling groove, for example. - As can be seen from
FIG. 3 , the first fixingelement 32 is provided in the form of three arms, wherein theindividual arms 38 are of beveled design to simplify the installation and positioning of thereturn spring 24. -
FIG. 4 shows an external view of the bottom 31 of thesecond piston 4. It is apparent that a second, centrally arranged fixingelement 39 in the form of a circular projection extends from an outer side of the bottom 31. This performs its function when, in accordance with the second embodiment described below and shown inFIG. 5 , themaster cylinder 1 has a sensor arrangement for monitoring the position and movement of thepiston 3, and amagnetic guide element 40 rests on thesecond piston 4. - The
magnetic guide element 40 illustrated inFIG. 5 rests by means of a flange-shapedportion 41 on the bottom 31 of thesecond piston 4. Provided in the flange-shapedportion 41 is arecess 42, which corresponds to thesecond fixing element 39 and by means of which themagnetic guide element 40 is fixed and positioned on thesecond piston 4. - The
magnetic guide element 40 additionally has a peg-shapedportion 43 which points in the opposite direction to thepeg 25 of thefirst piston 3 and which serves as a means for guiding apermanent magnet 44. - The
magnet 44 serves as a signal transmitter for a position transmitter and generates a magnetic field radially in the direction of a sensor element (not shown)—preferably in the form of a Hall-effect sensor, a magnetoresistive sensor or a reed contact—which is provided at a fixed location on thehousing 2 and can be connected to an electronic control unit (not shown) in order to permit position detection. - The
magnet 44 is ring-shaped and, as is apparent, is arranged betweendisks cylindrical support 47 made of nonmagnetic material, which has acollar 48 for axial support of themagnet 44. - As is apparent from
FIG. 5 , thesupport 47 with themagnet 44 is acted upon, on the one hand, by thereturn spring 23 of thefirst piston 3 and, on the other hand, by another spring means 49, which is supported on thesecond piston 4, with the result that themagnet 44 is as it were clamped between thepistons return spring 23 is greater than the spring force of the other spring means 49. This allows an actuation-induced displacement of themagnet 44, even if thesecond piston 4 is fixed immovably due to a regulating operation affecting the vehicle dynamics. - In addition to the improvement in dynamics, the embodiment described of the
second piston 4 in the two illustrative embodiments offers the additional advantages that, for example, the overall length of themaster cylinder 1 can be shortened by means of ashorter return spring 24, and themaster cylinder 1 has fewer individual components overall. It is furthermore also possible, within the scope of the invention, to design thefirst piston 3 with thecontrol passages 20 described in the form of axial grooves and with the first fixingelement 32. -
FIGS. 6 and 7 show apiston 50 of a third illustrative embodiment, which can be provided as a first and/or as a second piston of themaster cylinder 1. As is apparent especially fromFIG. 7 , which shows an enlarged detail of thepiston 50,control passages 51 of thepiston 50 have acontrol edge 52 formed parallel to apiston end face 53. In contrast to the first two illustrative embodiments, thecontrol passages 51 are provided as radial apertures in thepiston 50, which can be produced from plastic or by means of an extrusion process, as described above. Here too, theparallel control edge 52 has the advantage that the flow cross section of thecontrol passages 52 can be enlarged while keeping the closing travel the same, thus improving the dynamic behavior of themaster cylinder 1 during control interventions. The remaining shape of thecontrol passages 51 can be adapted to the corresponding characteristics of the piston. - Another illustrative embodiment, which is not shown, envisages that the control passages begin radially and continue as a groove which extends axially under the sealing element.
-
- 1 master cylinder
- 2 housing
- 3 piston
- 4 piston
- 5 annular groove
- 6 annular groove
- 7 sealing element
- 8 sealing element
- 9 inner sealing lip
- 10 inner sealing lip
- 11 outer sealing lip
- 12 outer sealing lip
- 13 outer side
- 14 outer side
- 15 pressure chamber
- 16 pressure chamber
- 17 replenishment chamber
- 18 replenishment chamber
- 19 control passage
- 20 control passage
- 21 wall
- 22 wall
- 23 return spring
- 24 return spring
- 25 peg
- 26 end
- 27 stop
- 28 sleeve
- 29 collar
- 30 collar
- 31 bottom
- 32 fixing element
- 33 control edge
- 34 control edge
- 35 inner groove
- 36 piston end face
- 37 collar heel
- 38 arm
- 39 fixing element
- 40 magnetic guide element
- 41 flange-shaped portion
- 42 recess
- 43 peg-shaped portion
- 44 magnet
- 45 disk
- 46 disk
- 47 support
- 48 collar
- 49 spring means
- 50 piston
- 51 control passage
- 52 control edge
- 53 piston end face
- 54 groove end
- A actuating direction
Claims (10)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009054695.2 | 2009-12-15 | ||
DE102009054695A DE102009054695A1 (en) | 2009-12-15 | 2009-12-15 | Master cylinder for a regulated braking system |
DE102009054695 | 2009-12-15 | ||
PCT/EP2010/069729 WO2011082999A1 (en) | 2009-12-15 | 2010-12-15 | Master cylinder for a regulated braking system |
Publications (2)
Publication Number | Publication Date |
---|---|
US20130213033A1 true US20130213033A1 (en) | 2013-08-22 |
US9657752B2 US9657752B2 (en) | 2017-05-23 |
Family
ID=43754702
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/515,898 Active 2033-09-21 US9657752B2 (en) | 2009-12-15 | 2010-12-15 | Master cylinder for a regulated braking system |
Country Status (8)
Country | Link |
---|---|
US (1) | US9657752B2 (en) |
EP (1) | EP2512888B1 (en) |
JP (1) | JP5976545B2 (en) |
KR (2) | KR20120099767A (en) |
CN (1) | CN102656069B (en) |
BR (1) | BR112012014563B1 (en) |
DE (1) | DE102009054695A1 (en) |
WO (1) | WO2011082999A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140165553A1 (en) * | 2010-12-21 | 2014-06-19 | Marc Rodriguez | Primary piston for a tandem master cylinder and tandem master cylinder equipped with such a primary piston |
US20140182283A1 (en) * | 2012-12-28 | 2014-07-03 | Nissin Kogyo Co., Ltd. | Hydraulic pressure generator |
US9452745B2 (en) | 2011-05-05 | 2016-09-27 | Continental Teves Ag & Co. Ohg | Master cylinder, in particular for a controlled brake system |
US20170088107A1 (en) * | 2015-09-25 | 2017-03-30 | Mando Corporation | Master cylinder for brake system |
US11370403B2 (en) | 2017-12-22 | 2022-06-28 | Continental Teves Ag & Co. Ohg | Unit having at least one piston with an associated piston spring |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2989045A1 (en) * | 2012-04-06 | 2013-10-11 | Bosch Gmbh Robert | Primary piston for tandem master braking cylinder of car, has hole comprising inner surface whose intersection point is located in front of another intersection point of inner surface of hole and of inner surface of piston |
DE102012014321A1 (en) * | 2012-07-19 | 2014-01-23 | Lucas Automotive Gmbh | Master brake cylinder for a motor vehicle brake system with profiled pressure piston |
JP5919155B2 (en) * | 2012-09-26 | 2016-05-18 | 日信工業株式会社 | Hydraulic master cylinder and method of manufacturing piston of hydraulic master cylinder |
CN104955693A (en) * | 2013-01-30 | 2015-09-30 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Master brake cylinder for a hydraulic motor vehicle brake system |
EP2951068B1 (en) * | 2013-01-30 | 2019-05-15 | Continental Teves AG & Co. OHG | Master vehicle brake cylinder |
FR3007721B1 (en) | 2013-06-27 | 2016-11-11 | Bosch Gmbh Robert | TANDEM MASTER CYLINDER PRIMARY PISTON |
DE102014215722A1 (en) * | 2013-09-04 | 2015-03-05 | Schaeffler Technologies Gmbh & Co. Kg | Master cylinder |
DE102013220738A1 (en) * | 2013-10-14 | 2015-04-16 | Continental Teves Ag & Co. Ohg | Master brake cylinder for a hydraulic brake system |
DE102016223760A1 (en) * | 2016-11-30 | 2018-05-30 | Robert Bosch Gmbh | Master brake cylinder, brake system |
DE102016224756A1 (en) * | 2016-12-12 | 2018-06-14 | Continental Teves Ag & Co. Ohg | Hydraulic unit with a piston |
DE102018201727A1 (en) * | 2018-02-05 | 2019-08-08 | Lucas Automotive Gmbh | Method for producing a brake force device for a vehicle brake system and such a brake force device |
JP2020055398A (en) * | 2018-10-01 | 2020-04-09 | 株式会社アドヴィックス | Master cylinder |
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-
2009
- 2009-12-15 DE DE102009054695A patent/DE102009054695A1/en not_active Withdrawn
-
2010
- 2010-12-15 BR BR112012014563-0A patent/BR112012014563B1/en active IP Right Grant
- 2010-12-15 CN CN201080056475.2A patent/CN102656069B/en active Active
- 2010-12-15 JP JP2012543711A patent/JP5976545B2/en active Active
- 2010-12-15 EP EP10796360.5A patent/EP2512888B1/en active Active
- 2010-12-15 US US13/515,898 patent/US9657752B2/en active Active
- 2010-12-15 WO PCT/EP2010/069729 patent/WO2011082999A1/en active Application Filing
- 2010-12-15 KR KR1020127017940A patent/KR20120099767A/en active Application Filing
- 2010-12-15 KR KR1020177001913A patent/KR20170010915A/en not_active Application Discontinuation
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US4998461A (en) * | 1988-03-08 | 1991-03-12 | Nippon Air Brake Co., Ltd. | Two-part plastic piston with excess resin receiving groove |
US4945728A (en) * | 1989-06-26 | 1990-08-07 | General Motors Corporation | Center compensating tandem master cylinder with seals in cylinder wall |
US20090210124A1 (en) * | 2003-12-09 | 2009-08-20 | Continental Teves Ag & Co. Ohg | Method and device for controlling a motor vehicle comprising an electronically controlled brake system with driving dynamics control |
US20050268608A1 (en) * | 2004-06-04 | 2005-12-08 | Zf Friedrichshafen Ag | Hydraulic cylinder |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140165553A1 (en) * | 2010-12-21 | 2014-06-19 | Marc Rodriguez | Primary piston for a tandem master cylinder and tandem master cylinder equipped with such a primary piston |
US9643579B2 (en) * | 2010-12-21 | 2017-05-09 | Robert Bosch Gmbh | Primary piston for a tandem master cylinder and tandem master cylinder equipped with such a primary piston |
US9452745B2 (en) | 2011-05-05 | 2016-09-27 | Continental Teves Ag & Co. Ohg | Master cylinder, in particular for a controlled brake system |
US20140182283A1 (en) * | 2012-12-28 | 2014-07-03 | Nissin Kogyo Co., Ltd. | Hydraulic pressure generator |
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US20170088107A1 (en) * | 2015-09-25 | 2017-03-30 | Mando Corporation | Master cylinder for brake system |
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US11370403B2 (en) | 2017-12-22 | 2022-06-28 | Continental Teves Ag & Co. Ohg | Unit having at least one piston with an associated piston spring |
Also Published As
Publication number | Publication date |
---|---|
DE102009054695A1 (en) | 2011-06-16 |
JP2013513525A (en) | 2013-04-22 |
JP5976545B2 (en) | 2016-08-23 |
BR112012014563A2 (en) | 2016-08-16 |
EP2512888B1 (en) | 2017-09-13 |
EP2512888A1 (en) | 2012-10-24 |
KR20120099767A (en) | 2012-09-11 |
KR20170010915A (en) | 2017-02-01 |
US9657752B2 (en) | 2017-05-23 |
BR112012014563B1 (en) | 2020-12-15 |
CN102656069B (en) | 2015-06-24 |
CN102656069A (en) | 2012-09-05 |
WO2011082999A1 (en) | 2011-07-14 |
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